US4436314A - Slide ring seal with spring to radially bias in opposite radial directions - Google Patents

Slide ring seal with spring to radially bias in opposite radial directions Download PDF

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Publication number
US4436314A
US4436314A US06/422,191 US42219182A US4436314A US 4436314 A US4436314 A US 4436314A US 42219182 A US42219182 A US 42219182A US 4436314 A US4436314 A US 4436314A
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United States
Prior art keywords
slide ring
spring
ring seal
bellows
turns
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Expired - Lifetime
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US06/422,191
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English (en)
Inventor
Paul Vossieck
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SKF Sealing Solutions GmbH
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Goetze GmbH
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Assigned to GOETZE AG.M D-5093 BURSCHEID, reassignment GOETZE AG.M D-5093 BURSCHEID, ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: VOSSIECK, PAUL
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Publication of US4436314A publication Critical patent/US4436314A/en
Assigned to GOETZE ELASTOMERE GMBH reassignment GOETZE ELASTOMERE GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GOETZE GMBH
Assigned to GOETZE GMBH reassignment GOETZE GMBH CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: GOETZE AG
Assigned to CR ELASTOMERE GMBH reassignment CR ELASTOMERE GMBH CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: GOETZE ELASTOMERE GMBH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/36—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member connected by a diaphragm or bellow to the other member

Definitions

  • the present invention relates to seals for sealing relatively rotating machine parts and, more particularly, a slide ring seal of the type comprising a slide ring having a central axis and a circumferential face, a tubular sleeve member formed of a bellows which encircles and engages at least a portion of the circumferential face of the slide ring and an adhering part constituting an integral continuation of the bellows and extending in a generally axial direction away from the slide ring.
  • the slide ring seal further comprises an approximately conically wound compression spring positioned within the tubular sleeve member in the zone of the adhering part and the bellows.
  • a slide ring seal of this type is known from German Offenlegungschrift (Application Published Without Examination) No. 2,921,669.
  • a support housing provided in the zone of the inner circumferential face of the adhering part serves to radially shape the latter.
  • a cylindrical compression spring extends axially between the support housing and the bellows. In the zone of the bellows, the slide ring is radially clamped in such a manner that the diameter of the bellows is larger than the inner diameter of the spring turns.
  • a slide ring seal of similar construction as described above is shown in British Pat. No. 888,118.
  • This structure has no support housing; its function is assumed by a compression spring which includes an initial cylindrical portion and a stepped, approximately conical portion. The spring turn of smallest diameter engages a groove formed in the bellows axially adjacent the slide ring. Apart from the complex shape of the bellows, a transmission of torque from slide ring to the adhering part is poor, since the spring merely carries out guiding functions.
  • German Gebrauchsmuster (Utility Model) No. 1,858,504 discloses a slide ring seal in which the end turns of the cylindrical spring surround the bellows and further, on one side the spring exerts a radial pressure on the slide ring and, when installed, it exerts, on the other side, a radial pressure on the shaft with the intermediary of the bellows.
  • the diameter of the bellows is larger than the inner diameter of the spring turns.
  • the bellows is radially so thick that the spring cannot exert any radial force on the shaft; rather, this force is applied by the bellows itself since in seals of this type the inner diameter of the elastomer member is, as a rule, designed to be smaller than the diameter of the shaft.
  • the elastomer member expands when it is axially pressed onto the shaft and circumferentially engages the same under internal radial tension.
  • this is achieved by providing a spring having at least three turns which are arranged on different radial planes within the shaft seal.
  • the spring turns having the smallest and the largest diameter cooperate with the adhering part and with that portion of the bellows which carries the slide ring to radially bias the slide ring seal in opposite directions.
  • the slide ring is securely held in the bellows and in the installed state, the adhering part is pressed into a corresponding receiving bore.
  • the radial spring forces are preferably greater in the installed state of the slide ring seal than prior to installation.
  • the spring has three turns and the middle turn has a radial height which corresponds to about the average radial height of the other two spring turns and is positioned preferably in the middle of the axial distance between the other two turns.
  • the compression spring is designed such that two or more consecutive turns are provided in the zone of the adhering part and/or in the zone of the bellows and are so wound that they are axially biased with respect to one another. This advantageously results in a stable spring configuration in those zones, ensuring that the slide ring seal is securely pressed into the receiving bore, thus preventing the elastomer adhering part from sliding off the spring and that canting is securely eliminated. It is a further feature of the invention that the above mentioned consecutive turns of the compression spring all exert radial forces on the circumferential faces of the corresponding parts of the slide ring seal thus ensuring a positive transmission of torque, even in extreme situations.
  • the turns of the compression spring positioned in the zone of the adhering part and/or in the zone of the bellows is eccentrically wound in such a manner that the turns, starting from the end face of the adhering part and/or the bellows are wound larger or smaller radially in the direction of the respective circumferential face.
  • At least the first two turns of the compression spring positioned in the zone of the adhering part and/or in the zone of the bellows are affixed to each other.
  • the compression spring exerts a greater radial force on the adhering part than on the bellows in order to compensate for any malfunctions that may occur during the operation.
  • the invention ensures that, due to the elasticity of the spring, the mounting (axial pressing-in) of the slide ring seal is relatively easy and that the adhering part, due to the radially acting spring force, fits well into the receiving bore and that there also is a good transmission of torque from the slide ring to the adhering part.
  • cross-sectional shape of the spring wire may be determined dependent upon the particular operational environment.
  • FIG. 1 is an axial sectional view of a preferred embodiment of the invention.
  • FIG. 2 is an axial sectional view of another preferred embodiment of the invention.
  • FIG. 2a is an axial sectional view of a variant of a component forming part of the structure illustrated in FIG. 2.
  • FIG. 3 is an axial sectional view of a further preferred embodiment of the invention.
  • the slide ring seal shown in FIG. 1 comprises a slide ring 1 having a slide face 2 and, remote therefrom, a stepped length portion of reduced diameter including a circumferential face 3.
  • a sleeve member 4' includes a bellows 4 whose end encircles the face 3 of the slide ring 1 and an adhering part 8 integral with and being an axial continuation of the bellows 4.
  • the bellows 4 includes a front portion 4" which is radially adjacent the slide ring 1 and which has an approximately U-shaped cross-sectional profile. The bellows 4 then continues in a substantially radial portion, having bulging part 5.
  • a circumferential zone 6 extends from the bulging part 5 generally parallel to the central axis of slide ring 1 and is adjoined by an axial abutment 7, from which axially extends the adhering part 8.
  • the latter is provided with an undulated surface 9 for the purpose of assuring better clamping in its receiving member (not shown).
  • the adhering part 8 includes an end face 10, a holding claw 11 formed integrally with the end face 10 and oriented radially inwardly.
  • a compression spring 12 is located within sleeve member 4' and is positioned axially between adhering part 8 and the U-shaped portion 4" of bellows 4. When the slide ring seal is in the installed state, compression spring 12 generates the axial force required to hold the slide ring 1 sealingly against a counter ring or a corresponding sealing face (not shown).
  • Spring 12 is approximately conical and has a rectangular wire cross section.
  • the individual spring turns 13, 14 and 15 of spring 12 are arranged in different radial and axial planes. The turns 13 and 15, which are effective in opposite directions, exert a defined radial force on the bellows 4 and on the adhering part 8, respectively.
  • the slide ring 1 is held radially secure by the bellows 4 and the adhering part 8, in the mounted state of the slide ring seal, is securely held in the receptacle member. Moreover, an optimum transmission of torque between the slide ring 1 and the adhering part 8 is assured without any additional parts.
  • FIG. 2 the slide ring 1 and the sleeve member formed of bellows 4 and adhering part 8 are identical to the FIG. 1 embodiment.
  • the FIG. 2 embodiment comprises a generally conical spring 16 having a circular wire cross section.
  • spring turns 20, 21 are provided, respectively, adjacent adhering part 8 as well as adjacent U-shaped portion 4" of bellows 4.
  • turns 20 and 21 are so wound that an axial bias prevails between turns 20 and 17 and between turns 21 and 19.
  • the spring 16 has the purpose to radially press bellows 4 against the slide ring 1 and to ensure a secure seating of the adhering part 8 in the receiving member.
  • the spring turns 19 and 21 are connected to one another in several places along their circumference by means of spot welds 22.
  • FIG. 2a shows a further variation of the conical spring 16 of the FIG. 2 embodiment.
  • Spring 16a is provided with three turns 23, 24, 25 positioned adjacent the adhering part (not shown in FIG. 2a).
  • the turns 24 and 25 have the same diameter and are symmetrical with the spring axis, while the turn 23 is wound eccentrically thereto in the direction of the adhering member.
  • the slide ring seal 26 has a tubular sleeve member, whose adhering part 27 is radially pressed against a shaft 28.
  • a spring 29 exerts radially opposite forces on the bellows 31 which in this embodiment is positioned in slide ring 30 and on the adhering part 27.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Sealing (AREA)
  • Sealing Devices (AREA)
US06/422,191 1982-01-25 1982-09-23 Slide ring seal with spring to radially bias in opposite radial directions Expired - Lifetime US4436314A (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3202274 1982-01-25
DE3202274 1982-01-25
DE3222759A DE3222759C2 (de) 1982-01-25 1982-06-18 Gleitringdichtung
DE3222759 1982-06-18

Publications (1)

Publication Number Publication Date
US4436314A true US4436314A (en) 1984-03-13

Family

ID=25799073

Family Applications (1)

Application Number Title Priority Date Filing Date
US06/422,191 Expired - Lifetime US4436314A (en) 1982-01-25 1982-09-23 Slide ring seal with spring to radially bias in opposite radial directions

Country Status (4)

Country Link
US (1) US4436314A (de)
EP (1) EP0084596B1 (de)
DE (1) DE3222759C2 (de)
ES (1) ES279733Y (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080048400A1 (en) * 2006-08-28 2008-02-28 Freudenberg-Nok General Partnership Unitized seal with integral flanged sleeve
US20110290925A1 (en) * 2010-05-03 2011-12-01 Sandvik Intellectual Property Ab Dust seal for gyratory crusher
RU168600U1 (ru) * 2016-05-04 2017-02-10 Общество с ограниченной ответственностью Научно-производственное предприятие "Вектор" Торцевое уплотнение вращающегося вала

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3436715C1 (de) * 1984-10-06 1985-10-10 Goetze Ag, 5093 Burscheid Gleitringdichtung
DE3703533A1 (de) * 1987-02-06 1988-08-25 Goetze Ag Gleitringdichtung
DE4225810C2 (de) * 1992-08-05 1995-06-14 Roland Man Druckmasch Falzzylinder
DE19801112A1 (de) 1997-01-17 1998-07-23 Miele & Cie Gleitringdichtung

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2328160A (en) * 1940-03-29 1943-08-31 Gen Motors Corp Fluid sealing device
US2646296A (en) * 1944-06-14 1953-07-21 Destoumieux Paul Packing for use between rotatable and fixed parts
FR1144001A (fr) * 1944-06-14 1957-10-08 Joint d'étanchéité entre parties tournante et fixe
US2440394A (en) * 1944-10-11 1948-04-27 Apex Electrical Mfg Co Liquid seal device
GB631981A (en) * 1947-06-27 1949-11-14 Morgan Crucible Co Improvements in or relating to sealing devices for relatively rotatable parts
IT527712A (de) * 1953-06-08
DE1051087B (de) * 1955-03-14 1959-02-19 Kupfer Asbest Co Gleitringdichtung
DE1850250U (de) * 1958-07-04 1962-04-19 Super Oil Seals & Gaskets Ltd Dichtung fuer zwei teile mit relativbewegung.
GB888118A (en) * 1959-06-24 1962-01-24 J & J Hillman Ltd Improvements in face seals for sealing between relatively rotating parts
DE1858504U (de) * 1960-03-12 1962-09-13 Kupfer Asbest Co Einbaufertige gleitringdichtung.
FR2122041A5 (de) * 1971-01-15 1972-08-25 Meca Ind Int
FR2436305A1 (fr) * 1978-09-14 1980-04-11 Mecanique Ind Int Dispositif d'etancheite entre une partie fixe et un arbre tournant
DE2921669C2 (de) * 1979-05-29 1982-12-30 Kaco Gmbh + Co, 7100 Heilbronn Dichtung

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080048400A1 (en) * 2006-08-28 2008-02-28 Freudenberg-Nok General Partnership Unitized seal with integral flanged sleeve
US20110290925A1 (en) * 2010-05-03 2011-12-01 Sandvik Intellectual Property Ab Dust seal for gyratory crusher
US8646712B2 (en) * 2010-05-03 2014-02-11 Sandvik Intellectual Property Ab Dust seal for gyratory crusher
AU2011249096B2 (en) * 2010-05-03 2014-11-13 Sandvik Intellectual Property Ab Gyratory crusher comprising a dust seal and method of fitting
RU168600U1 (ru) * 2016-05-04 2017-02-10 Общество с ограниченной ответственностью Научно-производственное предприятие "Вектор" Торцевое уплотнение вращающегося вала

Also Published As

Publication number Publication date
DE3222759C2 (de) 1985-10-31
EP0084596A1 (de) 1983-08-03
DE3222759A1 (de) 1983-08-11
ES279733U (es) 1985-06-01
EP0084596B1 (de) 1986-12-30
ES279733Y (es) 1988-06-16

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